CN205618406U - Impeller subassembly, centrifugal fan and smoke ventilator - Google Patents
Impeller subassembly, centrifugal fan and smoke ventilator Download PDFInfo
- Publication number
- CN205618406U CN205618406U CN201620384183.6U CN201620384183U CN205618406U CN 205618406 U CN205618406 U CN 205618406U CN 201620384183 U CN201620384183 U CN 201620384183U CN 205618406 U CN205618406 U CN 205618406U
- Authority
- CN
- China
- Prior art keywords
- impeller
- equal
- spiral case
- degree
- diffusion portion
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The utility model provides an impeller subassembly, centrifugal fan and smoke ventilator, wherein, the impeller subassembly includes: the impeller, first diffusion portion, first diffusion portion sets up the one side at the impeller along the axial direction of impeller, second diffusion portion, second diffusion portion sets up the opposite side at the impeller along the axial direction of impeller, and first diffusion portion and second diffusion portion all are horn shaped structure, and the opening sectional area of first diffusion portion and second diffusion portion is all crescent along the direction of keeping away from the impeller, form first diffusion angle beta 1 between the extending direction of first diffusion portion and impeller radial, formation second diffusion angle beta 2 between the extending direction of second diffusion portion and impeller radial, wherein, first diffusion angle beta 1 more than or equal to 30 degree and less than or equal to 45 degree, second diffusion angle beta 2 more than or equal to 30 degree and less than or equal to 50 degree. The utility model provides a smoke ventilator's among the prior art centrifugal fan's the problem that the biggest static pressure is low.
Description
Technical field
This utility model relates to smoke exhaust ventilator technical field, in particular to a kind of impeller assembly, centrifugal blower and smoke pumping
Machine.
Background technology
In existing smoke exhaust ventilator technical field, in order to meet the use demand of high residential building user, the smoking effect of smoke exhaust ventilator
In urgent need to be improved.At present, the mode of the smoking effect improving smoke exhaust ventilator generally has two kinds:
A kind of mode is the convulsion amount of the centrifugal blower improving smoke exhaust ventilator, and another way is to increase the centrifugal blower of smoke exhaust ventilator
Maximum static pressure.
The technology of the convulsion amount improving centrifugal blower is the most ripe, but while using this kind of mode to improve smoking effect, can not
Energy consumption can be increased with avoiding.And use the mode of maximum static pressure increasing centrifugal blower to improve the technology of smoking effect of smoke exhaust ventilator
The most immature.
At present, by the way of using direct current generator to replace alternating current generator, the maximum static pressure of centrifugal blower is typically increased, so to carry
The rotating speed upper limit of high motor, reaches to increase the effect of centrifugal blower maximum static pressure.But, owing to the energy consumption of direct current generator is relatively big,
So that use cost significantly improves, but also the price causing smoke exhaust ventilator is the most prohibitively expensive, adds selling price,
Thus had a strong impact on the sales volume of smoke exhaust ventilator.
Therefore, in the installing space of limited smoke exhaust ventilator, ensure that low energy consumption does not increase the use of smoke exhaust ventilator simultaneously
On the premise of cost, the technology improving centrifugal blower maximum static pressure by being optimized the structure of centrifugal blower urgently breaks through.
Utility model content
Main purpose of the present utility model is to provide a kind of impeller assembly, centrifugal blower and smoke exhaust ventilator, to solve prior art
In the low problem of the maximum static pressure of centrifugal blower of smoke exhaust ventilator.
To achieve these goals, according to an aspect of the present utility model, it is provided that a kind of impeller assembly, impeller assembly includes:
Impeller；First diffusion portion, the first diffusion portion is arranged on the side of impeller along the axial direction of impeller；Second diffusion portion, second expands
Splenium is arranged on the opposite side of impeller along the axial direction of impeller, the first diffusion portion and the second diffusion portion all in horn-like structure, and
The opening section in the first diffusion portion and the second diffusion portion is long-pending to be all gradually increased along the direction away from impeller；The extension side in the first diffusion portion
The first diffusion angle beta is formed between the radial direction of impeller1, between bearing of trend and the radial direction of impeller in the second diffusion portion, form the
Two diffusion angle betas2, wherein, the first diffusion angle beta1More than or equal to 30 degree and less than or equal to 45 degree, the second diffusion angle beta2Greatly
In equal to 30 degree and less than or equal to 50 degree.
Further, the diameter D of the first diffusion periphery away from impeller side in the first diffusion portion1With the second diffusion portion away from leaf
The equal diameters of the second diffusion periphery of wheel side.
Further, impeller has the spaced multiple blades of central axis around impeller, each blade away from central axis
Distance between first end and central axis is equal, and the number of blade is more than or equal to 60 and less than or equal to 80.
Further, impeller has the spaced multiple blades of central axis around impeller, in central axis is in horizontal plane
Time, the first end away from central axis being positioned at a blade at the peak of impeller in multiple blades and close central axis
The second end between line projection and horizontal plane in the plane being perpendicular to central axis between angle form blade pitch angle
β3, blade lean angle beta3More than or equal to 45 degree and less than or equal to 60 degree, first end away from central axis of blade is being perpendicular to
Tangent line G at subpoint in the plane of central axis1Front G with blade2Between formed the outlet that obtuse angle is impeller install
Angle beta4, exit installation angle β4More than or equal to 160 degree and less than 180 degree, the second end of the close central axis of blade is being perpendicular to
Tangent line H at subpoint in the plane of central axis1Front H with blade2Between formed the import that acute angle is impeller install
Angle beta5, stagger angle β5More than or equal to 60 degree and less than 90 degree.
Further, the impeller outer diameter D of impeller2More than or equal to 250 millimeters and less than or equal to 276 millimeters.
Further, the impeller outer diameter D of impeller2It it is 256 millimeters.
According to another aspect of the present utility model, it is provided that a kind of centrifugal blower, including spiral case and impeller assembly, spiral case has sky
Chamber, impeller assembly is arranged in the cavity of spiral case, and impeller assembly is above-mentioned impeller assembly, before cavity is by spiral case coaming plate, spiral case
Plate and spiral case back plate surround jointly, before the spiral case of the close spiral case that the first diffusion portion of impeller assembly is arranged on the impeller of impeller assembly
The side of plate, the second diffusion portion of impeller assembly is arranged on the side of the spiral case back plate of the close spiral case of impeller.
Further, distance W between two intersection points of the molded line of the end of a period cross section of spiral case and spiral case2More than or equal to 365 millimeters and
Less than or equal to 395 millimeters.
Further, distance W between two intersection points of the molded line of the end of a period cross section of spiral case and spiral case2It it is 378 millimeters.
Further, spiral case coaming plate has first paragraph, second segment and the 3rd section being connected, and second segment is the snail tongue section of arc surfaced,
The arc radius r of snail tongue section is more than or equal to 4.5 millimeters and less than or equal to 15 millimeters.
According to another aspect of the present utility model, it is provided that a kind of smoke exhaust ventilator, including centrifugal blower, centrifugal blower is above-mentioned
Centrifugal blower.
Application the technical solution of the utility model, on the premise of the rotating speed of the alternating current generator without changing centrifugal blower, by inciting somebody to action
First diffusion angle beta1Between being disposed greater than equal to 30 degree and being less than or equal to 45 degree, simultaneously by the second diffusion angle beta2It is arranged on
More than or equal to 30 degree and less than or equal between 50 degree, so that the maximum static pressure of centrifugal blower maintains 408Pa extremely effectively
Between 448Pa.So, it is effectively improved the suitability between impeller and spiral case with the first diffusion portion and the second diffusion portion,
Improve the assembling convenience of centrifugal blower, the maximum static pressure of centrifugal blower maintains the scope of high value simultaneously, thus effectively
Increase the intensity of draft of centrifugal blower, and then reach the purpose of the smoking effect strengthening smoke exhaust ventilator.
Accompanying drawing explanation
The Figure of description of the part constituting the application is used for providing being further appreciated by of the present utility model, of the present utility model
Schematic description and description is used for explaining this utility model, is not intended that improper restriction of the present utility model.In the accompanying drawings:
Fig. 1 shows the front view of the spiral case of the centrifugal blower according to a kind of alternative embodiment of the present utility model；
Fig. 2 shows the molded line schematic diagram of the spiral case of the centrifugal blower in Fig. 1；
Fig. 3 shows the right view of the spiral case of the centrifugal blower in Fig. 1；
Fig. 4 show the centrifugal blower according to a kind of alternative embodiment of the present utility model with the first diffusion portion and the second diffusion
The structural representation of the impeller in portion；
Fig. 5 shows the top view of the impeller in the alternative embodiment of Fig. 4；
Fig. 6 shows another top view of the impeller in Fig. 4 in alternative embodiment.
Wherein, above-mentioned accompanying drawing includes the following drawings labelling:
10, spiral case；11, spiral case coaming plate；111, first paragraph；112, second segment；113, the 3rd section；12, spiral case header board；
13, spiral case back plate；14, end of a period cross section；15, molded line；151, the first tangent line；152, the second tangent line；16, air outlet；
20, impeller；21, central axis；22, blade；30, the first diffusion portion；31, the first diffusion periphery；40, the second diffusion
Portion；41, the second diffusion periphery.
Detailed description of the invention
It should be noted that in the case of not conflicting, the embodiment in the application and the feature in embodiment can be mutually combined.
Describe this utility model below with reference to the accompanying drawings and in conjunction with the embodiments in detail.
It it is noted that described further below is all exemplary, it is intended to provide further instruction to the application.Unless otherwise finger
Bright, all technology used herein and scientific terminology have and are generally understood that with the application person of an ordinary skill in the technical field
Identical meanings.
In this utility model, in the case of illustrating on the contrary, the noun of locality of use such as " upper and lower " is typically for attached
For direction shown in figure, or for on vertical, vertical or gravity direction；Similarly, for ease of understand and
Describing, it is inside and outside that " inside and outside " refers to relative to the profile of each parts itself, but the above-mentioned noun of locality is not limited to this practicality
Novel.
The problem low in order to solve the maximum static pressure of the centrifugal blower of smoke exhaust ventilator of the prior art, this utility model provides one
Planting impeller assembly, centrifugal blower and smoke exhaust ventilator, wherein, impeller assembly is following impeller assembly.
As shown in Figure 4, impeller assembly includes impeller the 20, first diffusion portion 30 and the second diffusion portion 40, the first edge, diffusion portion 30
The axial direction of impeller 20 is arranged on the side of impeller 20, and the second diffusion portion 40 is arranged on impeller along the axial direction of impeller 20
The opposite side of 20, the first diffusion portion 30 and the second diffusion portion 40 are all in horn-like structure, and the first diffusion portion 30 and the second diffusion
The opening section in portion 40 is long-pending to be all gradually increased along the direction away from impeller 20；The bearing of trend in the first diffusion portion 30 and impeller 20
Radial direction between form the first diffusion angle beta1, between bearing of trend and the radial direction of impeller 20 in the second diffusion portion 40, form second
Diffusion angle beta2, wherein, the first diffusion angle beta1More than or equal to 30 degree and less than or equal to 45 degree, the second diffusion angle beta2It is more than
Equal to 30 degree and less than or equal to 50 degree.
On the premise of the rotating speed of the alternating current generator without changing centrifugal blower, by by the first diffusion angle beta1It is disposed greater than
In 30 degree and less than or equal between 45 degree, simultaneously by the second diffusion angle beta2It is disposed greater than equal to 30 degree and less than or equal to 50
Between degree, so that the maximum static pressure of centrifugal blower maintains between 408Pa to 448Pa effectively.So, it is effectively improved
With the suitability between the first diffusion portion 30 and the impeller 20 in the second diffusion portion 40 and spiral case 10, improve centrifugal blower
Assembling convenience, the maximum static pressure of centrifugal blower maintains the scope of high value simultaneously, thus effectively increases centrifugal blower
The intensity of draft, and then reached to strengthen the purpose of smoking effect of smoke exhaust ventilator.
From substantial amounts of experiment conclusion, when the first diffusion angle beta1Or the second diffusion angle beta2During less than 30 degree, centrifugal blower
Maximum static pressure be in lower value all the time, centrifugal blower is in unstable working state, when the first diffusion angle beta1More than 45 degree or
Second diffusion angle beta2During more than 50 degree, it is not easy to impeller 20 is successfully installed to spiral case 10, reduces centrifugal blower
Practicality.
Alternatively, the first diffusion angle beta1With the second diffusion angle beta2It is 45 degree.First diffusion portion 30 away from impeller 20
The diameter D of the first diffusion periphery 31 of side1With the second diffusion periphery 41 away from impeller 20 side in the second diffusion portion 40
Equal diameters.So, impeller 20 symmetrically structure, it is effectively improved the maximum static pressure of centrifugal blower, but also convenient by leaf
Wheel 20 is assemblied in spiral case 10, improves the assembling convenience of centrifugal blower.
Still optionally further, the rotating speed of the alternating current generator of centrifugal blower is 1350 revs/min, the first diffusion portion in horn-like structure
30 a length of 10 millimeters of its bearing of trend, and the second diffusion portion 40 in horn-like structure is at a length of the 10 of its bearing of trend
Millimeter.So, while the maximum static pressure ensureing centrifugal blower is in high value, it is effectively improved impeller 20 and spiral case 10
Between suitability is installed, and make the overall dimensions of centrifugal blower be in the range of reasonably.
When the rotating speed of the alternating current generator of centrifugal blower is 1350 revs/min, the first diffusion angle beta1, the second diffusion angle beta2With
The relation of the maximum static pressure of centrifugal blower is as shown in table 1 below.
Table 1. first diffusion angle beta1, the second diffusion angle beta2Relation table with the maximum static pressure of centrifugal blower
As seen from the above table, when the first diffusion angle beta1Between being disposed greater than equal to 30 degree and being less than or equal to 45 degree, the second diffusion
Angle beta2Time between being disposed greater than equal to 30 degree and being less than or equal to 50 degree, the maximum static pressure of centrifugal blower maintains effectively
Between 408Pa to 448Pa, centrifugal blower now is in efficient duty.
As depicted in figs. 1 and 2, the centrifugal blower that this utility model provides includes impeller assembly, motor and spiral case 10, impeller sets
Part is arranged in spiral case 10, and motor driven impeller assembly rotates, and spiral case 10 has cavity, and cavity is by spiral case coaming plate 11, spiral case
Header board 12 and spiral case back plate 13 surround jointly, and spiral case coaming plate 11 has first paragraph 111, the second segment 112 and the 3rd being connected
Section 113, second segment 112 is the snail tongue section of arc surfaced, and the arc radius r of snail tongue section is more than or equal to 4.5 millimeters and less than or equal to 15
Millimeter.The effect of snail tongue section is to prevent gas at spiral case 10 internal circulation flow.
On the premise of the rotating speed of the alternating current generator without changing centrifugal blower, only by improving the structure of spiral case 10, spiral case is enclosed
Between the arc radius r of the snail tongue section of plate 11 is disposed greater than equal to 4.5 millimeters and is less than or equal to 15 millimeters, so that centrifugal wind
The maximum static pressure of machine maintains between 415Pa to 436.7Pa effectively, is namely effectively increased the maximum static pressure of centrifugal blower.
Alternatively, the rotating speed of the alternating current generator of centrifugal blower is 1350 revs/min.
From substantial amounts of experiment conclusion, the maximum static pressure of centrifugal blower reduces with the increase of the arc radius r of snail tongue section, and works as
When the arc radius r of snail tongue section is more than 15 millimeters, the maximum static pressure of centrifugal blower drastically declines, and centrifugal blower is in unstable work
Making state, when the arc radius r of snail tongue section is less than 4.5 millimeters, the difficulty of the manufacturing process of the spiral case 10 of centrifugal blower is obvious
Increasing, the manufacturing cost of spiral case 10 dramatically increases, and have impact on the economy of centrifugal blower.
It follows that the optimum span of the arc radius r of the snail tongue section of spiral case coaming plate 11 is between 4.5 millimeters and 15 millimeters,
Centrifugal blower now is in optimum Working, and the maximum static pressure of centrifugal blower maintains a high value, thus by by snail
Between the arc radius r of the snail tongue section of shell coaming plate 11 is disposed greater than equal to 4.5 millimeters and is less than or equal to 15 millimeters, effectively control
Make manufacturing cost and the cost of use of smoke exhaust ventilator, reach the purpose of the smoking effect strengthening smoke exhaust ventilator simultaneously.
Alternatively, as it is shown on figure 3, the width W of spiral case 101It it is 175 millimeters.
Alternatively, distance W between two intersection points of the molded line 15 of the end of a period cross section 14 of spiral case 10 and spiral case 102It is more than or equal to
365 millimeters and less than or equal to 395 millimeters.
As depicted in figs. 1 and 2, the first tangent line 151 of the molded line 15 of spiral case 10 and the second tangent line 152 are each parallel to spiral case 10
End of a period cross section 14, and the first tangent line 151 relative to the second tangent line 152 away from the air outlet 16 of spiral case 10, the first tangent line 151
And the point of contact formed at the molded line 15 of spiral case 10 is to distance W between the outlet air surface of the air outlet 16 of spiral case 103It it is 373 millimeters.
By optimizing the width W of spiral case 10 further1Value, the molded line 15 of end of a period cross section 14 and spiral case 10 of spiral case 10
Two intersection points between distance W2Span and the first tangent line 151 and the molded line 15 of spiral case 10 at the point of contact that formed to snail
Distance W between the outlet air surface of the air outlet 16 of shell 103Value, so that it is determined that the monnolithic case physical dimension of spiral case 10,
Obtain the centrifugal blower that the size of spiral case 10 meets a series of models of above-mentioned scope, and by by the spiral case coaming plate of centrifugal blower
The arc radius r of the snail tongue section of 11 is arranged on rational scope, just can improve the maximum static pressure of the centrifugal blower of a series of model,
Thus increase the intensity of draft of centrifugal blower, and then reach the purpose of the smoking effect strengthening smoke exhaust ventilator.
Preferably, distance W between two intersection points of the molded line 15 of the end of a period cross section 14 of spiral case 10 and spiral case 102It is 378 millis
Rice.So, it is determined that the centrifugal blower of a kind of concrete model, when the rotating speed of the alternating current generator of centrifugal blower is 1350 revs/min,
The arc radius r of the snail tongue section of the spiral case coaming plate 11 of centrifugal blower is as shown in table 2 below with the relation of maximum static pressure.
The arc radius r of table 2. snail tongue section and the maximum static pressure relation table of centrifugal blower
| Arc radius r (millimeter) | 4.5 | 8 | 15 | 20 |
| Maximum static pressure (Pa) | 436.7 | 425 | 415 | 389 |
As shown in Figures 4 to 6, the impeller 20 of impeller assembly has the spaced multiple leaves of central axis 21 around impeller 20
Sheet 22, the distance between the first end away from central axis 21 and the central axis 21 of each blade 22 is equal, blade 22
Number is more than or equal to 60 and less than or equal to 80.So, the maximum static pressure of centrifugal blower maintains 425Pa to 455Pa effectively
Between.
On the premise of ensureing that the rotating speed of alternating current generator of centrifugal blower is constant, at identical impeller outer diameter D2With profile ID D3's
Under premise, by reasonably the number of blade 22 being arranged between 60 to 80, it is effectively increased the maximum of centrifugal blower
Static pressure, thus increase the intensity of draft of centrifugal blower, and then reached the purpose of the smoking effect strengthening smoke exhaust ventilator.
Specifically, when the rotating speed of the alternating current generator of centrifugal blower is 1350 revs/min, impeller outer diameter D2When being 256 millimeters,
The quantity of blade 22 is as shown in table 3 below with the relation of the maximum static pressure of centrifugal blower.
The relation table of the maximum static pressure of table 3. blade quantity and centrifugal blower
| Lobe numbers (individual) | 56 | 60 | 66 | 76 | 80 |
| Maximum static pressure (Pa) | 410.9 | 416 | 425 | 441.8 | 455 |
As seen from the above table, along with the increase of the quantity of blade 22, the maximum static pressure of centrifugal blower increases, it is contemplated that centrifugal wind
The quantity of the blade 22 of machine too much can cause the macroeconomic of centrifugal blower poor, and the quantity of blade too much can be to centrifugal wind
The intensity of draft of machine produces certain impact, when the span of the quantity of the blade 22 of centrifugal blower is between 60 to 80,
The maximum static pressure of centrifugal blower, while can producing the good intensity of draft, also significantly reduces centrifugal blower processing and manufacturing
Cost, thus reduce the overall price of smoke exhaust ventilator, it is possible to improve the sales volume of smoke exhaust ventilator well.
As shown in Figure 6, when central axis 21 is in horizontal plane, at the peak being positioned at impeller 20 in multiple blades 22
A blade 22 the first end away from central axis 21 and near central axis 21 the second end between line be perpendicular to
Angle between projection and horizontal plane in the plane of central axis 21 forms blade lean angle beta3, blade lean angle beta3It is more than
In 45 degree and less than or equal to 60 degree.
On the premise of ensureing that the rotating speed of alternating current generator of centrifugal blower is constant, by reasonably by blade lean angle beta3It is arranged on 45
Spend between 60 degree, thus ensure that centrifugal blower has enough maximum static pressures and can produce enough intensity of drafts, Jin Erda
Arrive the purpose of the smoking effect strengthening smoke exhaust ventilator.
From experimental data of the present utility model, the maximum static pressure of centrifugal blower is with blade lean angle beta3Reduction and increase, with
Time in view of installation difficulty between impeller 20 and spiral case 10, blade lean angle beta3Optimum span at 45 degree to 60 degree
Between.
As it is shown in figure 5, impeller 20 has the spaced multiple blades 22 of central axis 21 around impeller 20, blade 22
Away from the tangent line G at the first end of central axis 21 subpoint in the plane being perpendicular to central axis 211Volume with blade 22
Line G2Between formed the exit installation angle β that obtuse angle is impeller 204, exit installation angle β4More than or equal to 160 degree and less than 180
Degree.
Wherein, the front G of blade 222Outward flange camber line for blade 22 prolongs at the straight line of the end away from central axis 21
Long line.
On the premise of ensureing that the rotating speed of alternating current generator of centrifugal blower is constant, by reasonably by exit installation angle β4It is arranged on
Between 160 degree to 180 degree, thus ensure that centrifugal blower has enough maximum static pressures and can produce enough intensity of drafts, enter
And reached the purpose of the smoking effect strengthening smoke exhaust ventilator.
As it is shown in figure 5, impeller 20 has the spaced multiple blades 22 of central axis 21 around impeller 20, blade 22
Tangent line H at second end of close central axis 21 subpoint in the plane being perpendicular to central axis 211Volume with blade 22
Line H2Between formed the stagger angle β that acute angle is impeller 205, stagger angle β5More than or equal to 60 degree and less than 90 degree.
Wherein, the front H of blade 222For blade 22 outward flange camber line near central axis 21 the second end at straight line
Extended line.
On the premise of ensureing that the rotating speed of alternating current generator of centrifugal blower is constant, by reasonably by stagger angle β5It is arranged on 60
Spend between 90 degree, thus ensure that centrifugal blower has enough maximum static pressures and can produce enough intensity of drafts, Jin Erda
Arrive the purpose of the smoking effect strengthening smoke exhaust ventilator.
Specifically, when the rotating speed of the alternating current generator of centrifugal blower is 1350 revs/min, impeller outer diameter D2When being 256 millimeters,
The blade lean angle beta of impeller 203, exit installation angle β4, stagger angle β5As follows with the relation of the maximum static pressure of centrifugal blower
Shown in table 4.
Table 4. blade lean angle beta3, exit installation angle β4, stagger angle β5Relation table with the maximum static pressure of centrifugal blower
| Blade lean angle beta3 | 107 degree | 97 degree | 77 degree | 67 degree | 60 degree | 49 degree | 45 degree |
| Exit installation angle β4 | 122 degree | 132 degree | 152 degree | 160 degree | 172 degree | 180 degree | 180 degree |
| Stagger angle β5 | 11 degree | 23 degree | 47 degree | 60 degree | 70 degree | 80 degree | 90 degree |
| Maximum static pressure (Pa) | 237 | 287 | 361 | 392 | 425 | 472 | 485 |
When the rotating speed of the alternating current generator of centrifugal blower is 1350 revs/min, the impeller outer diameter D of impeller 202With centrifugal blower
The relation of big static pressure is as shown in table 5 below.
Table 5. impeller outer diameter D2Relation table with the maximum static pressure of centrifugal blower
| Impeller outer diameter D2(millimeter) | 220 | 240 | 250 | 256 | 276 | 280 |
| Maximum static pressure (Pa) | 293.5 | 370 | 415 | 425 | 502 | 520 |
As seen from the above table, the maximum static pressure of centrifugal blower is with the impeller outer diameter D of impeller 202Increase and increase, and centrifugal blower
Maximum static pressure and impeller outer diameter D2Square be directly proportional.
Alternatively, the impeller outer diameter D of impeller 202More than or equal to 250 millimeters and less than or equal to 276 millimeters.So, impeller is worked as
The impeller outer diameter D of 202Optimum span between 250 millimeters to 276 millimeters time, centrifugal blower is in optimum Working,
The maximum static pressure of centrifugal blower maintains a high value, thus effectively increases the intensity of draft of centrifugal blower, and then reaches
Strengthen the purpose of the smoking effect of smoke exhaust ventilator.
Still optionally further, the impeller outer diameter D of impeller 202It it is 256 millimeters.Impeller outer diameter D when impeller 202It it is 256 millimeters
Time, the spiral case 10 of the size adapting to impeller 20 also has the optimal installation dimension with smoke exhaust ventilator, facilitates centrifugal blower and take out
Assembling between lampblack absorber, thus while meeting the intensity of draft of centrifugal blower, improve the installation conveniency of smoke exhaust ventilator
And practicality.
The maximum static pressure of raising centrifugal blower, to improve the problem that the smoking effect of smoke exhaust ventilator is a system, is using alternating current
Machine in the case of ensureing that rotating speed is certain, by increasing the impeller outer diameter D of impeller2Or reduce blade lean angle beta3Can increase significantly
The maximum static pressure of big centrifugal blower.Moreover, by reduce centrifugal blower spiral case coaming plate 11 snail tongue section arc radius r or
Person increases the quantity of blade 22 or increases the exit installation angle β of impeller 204With stagger angle β5Or the first diffusion angle is set
Degree β1With the second diffusion angle beta2Between angular relationship etc., all can play the effect of maximum static pressure increasing centrifugal blower, this
Sample, while enhancing the smoking effect of smoke exhaust ventilator, significantly reduces the energy consumption of smoke exhaust ventilator, so that using smoke exhaust ventilator
Global design the most reasonable, improve user and to the experience of product and improve product competitiveness in the market.
It should be noted that term used herein above merely to describe detailed description of the invention, and be not intended to restricted root according to this Shen
Illustrative embodiments please.As used herein, unless the context clearly indicates otherwise, otherwise singulative is also intended to
Including plural form, additionally, it should be understood that, when using term " to comprise " in this manual and/or time " including ",
It indicates existing characteristics, step, work, device, assembly and/or combinations thereof.
It should be noted that term " first " in the description and claims of this application and above-mentioned accompanying drawing, " second " etc.
It is for distinguishing similar object, without being used for describing specific order or precedence.Should be appreciated that the data of so use
Can exchange in the appropriate case, in order to presently filed embodiment described herein can be with except here illustrating or describing
Order beyond those is implemented.
The foregoing is only preferred embodiment of the present utility model, be not limited to this utility model, for this area
For technical staff, this utility model can have various modifications and variations.All within spirit of the present utility model and principle, institute
Any modification, equivalent substitution and improvement etc. made, within should be included in protection domain of the present utility model.
Claims (11)
1. an impeller assembly, it is characterised in that described impeller assembly includes:
Impeller (20)；
First diffusion portion (30), described first diffusion portion (30) is arranged on described along the axial direction of described impeller (20)
The side of impeller (20)；
Second diffusion portion (40), described second diffusion portion (40) is arranged on described along the axial direction of described impeller (20)
The opposite side of impeller (20), described first diffusion portion (30) and described second diffusion portion (40) all in horn-like structure,
And the opening section in described first diffusion portion (30) and described second diffusion portion (40) is long-pending all along away from described impeller (20)
Direction be gradually increased；Formed between bearing of trend and the radial direction of described impeller (20) in described first diffusion portion (30)
First diffusion angle beta1, formed between bearing of trend and the radial direction of described impeller (20) in described second diffusion portion (40)
Second diffusion angle beta2, wherein, described first diffusion angle beta1More than or equal to 30 degree and less than or equal to 45 degree, described the
Two diffusion angle betas2More than or equal to 30 degree and less than or equal to 50 degree.
Impeller assembly the most according to claim 1, it is characterised in that described first diffusion portion (30) away from described impeller
(20) the diameter D of the first diffusion periphery (31) of side1With described second diffusion portion (40) away from described impeller (20)
The equal diameters of the second diffusion periphery (41) of side.
Impeller assembly the most according to claim 2, it is characterised in that described impeller (20) has around described impeller (20)
The spaced multiple blades of central axis (21) (22), each described blade (22) away from described central axis (21)
The first end and described central axis (21) between distance equal, the number of described blade (22) be more than or equal to 60
And less than or equal to 80.
Impeller assembly the most according to claim 1, it is characterised in that described impeller (20) has around described impeller (20)
The spaced multiple blades of central axis (21) (22), when described central axis (21) is in horizontal plane,
A described blade (22) at the peak being positioned at described impeller (20) in multiple described blades (22) away from
First end of described central axis (21) and the line between the second end of described central axis (21) are being perpendicular to
The angle between projection and described horizontal plane in the plane of described central axis (21) forms blade lean angle beta3, described
Blade lean angle beta3More than or equal to 45 degree and less than or equal to 60 degree, described blade (22) away from described central axis (21)
First end subpoint in the plane being perpendicular to described central axis (21) at tangent line G1With described blade (22)
Front G2Between formed the exit installation angle β that obtuse angle is described impeller (20)4, described exit installation angle β4It is more than
Equal to 160 degree and less than 180 degree, the second end of the close described central axis (21) of described blade (22) is vertically
Tangent line H at subpoint in the plane of described central axis (21)1Front H with described blade (22)2Between
The stagger angle β that acute angle is described impeller (20) formed5, described stagger angle β5More than or equal to 60 degree and little
In 90 degree.
Impeller assembly the most according to claim 1, it is characterised in that the impeller outer diameter D of described impeller (20)2It is more than or equal to
250 millimeters and less than or equal to 276 millimeters.
Impeller assembly the most according to claim 5, it is characterised in that the impeller outer diameter D of described impeller (20)2It is 256 millis
Rice.
7. a centrifugal blower, including spiral case (10) and impeller assembly, described spiral case (10) has cavity, described impeller assembly
It is arranged in the described cavity of described spiral case (10), it is characterised in that described impeller assembly is in claim 1 to 6
Impeller assembly described in any one, described cavity is by spiral case coaming plate (11), spiral case header board (12) and spiral case back plate (13)
Jointly surrounding, the first diffusion portion (30) of described impeller assembly is arranged on the close of the impeller (20) of described impeller assembly
The side of the spiral case header board (12) of described spiral case (10), the second diffusion portion (40) of described impeller assembly is arranged on institute
State the side of the spiral case back plate (13) of the close described spiral case (10) of impeller (20).
Centrifugal blower the most according to claim 7, it is characterised in that the end of a period cross section (14) of described spiral case (10) and institute
Distance W between two intersection points of the molded line (15) stating spiral case (10)2More than or equal to 365 millimeters and less than or equal to 395
Millimeter.
Centrifugal blower the most according to claim 8, it is characterised in that the end of a period cross section (14) of described spiral case (10) and institute
Distance W between two intersection points of the molded line (15) stating spiral case (10)2It it is 378 millimeters.
Centrifugal blower the most according to claim 9, it is characterised in that described spiral case coaming plate (11) has the first paragraph being connected
(111), second segment (112) and the 3rd section (113), described second segment (112) is the snail tongue section of arc surfaced, described snail
The arc radius r of tongue section is more than or equal to 4.5 millimeters and less than or equal to 15 millimeters.
11. 1 kinds of smoke exhaust ventilators, including centrifugal blower, it is characterised in that described centrifugal blower is any one of claim 7 to 10
Described centrifugal blower.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620384183.6U CN205618406U (en) | 2016-04-29 | 2016-04-29 | Impeller subassembly, centrifugal fan and smoke ventilator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620384183.6U CN205618406U (en) | 2016-04-29 | 2016-04-29 | Impeller subassembly, centrifugal fan and smoke ventilator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205618406U true CN205618406U (en) | 2016-10-05 |
Family
ID=57025373
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620384183.6U Active CN205618406U (en) | 2016-04-29 | 2016-04-29 | Impeller subassembly, centrifugal fan and smoke ventilator |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205618406U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109595186A (en) * | 2018-12-07 | 2019-04-09 | 佛山市南海九洲普惠风机有限公司 | A kind of air-foil fan |
-
2016
- 2016-04-29 CN CN201620384183.6U patent/CN205618406U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109595186A (en) * | 2018-12-07 | 2019-04-09 | 佛山市南海九洲普惠风机有限公司 | A kind of air-foil fan |
| CN109595186B (en) * | 2018-12-07 | 2023-09-19 | 佛山市南海九洲普惠风机有限公司 | High-efficiency fan |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN110118194B (en) | Axial flow wind wheel and air conditioner | |
| CN102032211B (en) | Biconical impeller for range hood | |
| CN106438466A (en) | Centrifugal fan and air-conditioner indoor unit | |
| WO2021063050A1 (en) | Fan and axial-flow impeller | |
| CN105782076A (en) | Centrifugal fan and kitchen ventilator | |
| CN205618406U (en) | Impeller subassembly, centrifugal fan and smoke ventilator | |
| CN205618407U (en) | Impeller subassembly, centrifugal fan and smoke ventilator | |
| CN205618392U (en) | Centrifugal fan and smoke ventilator | |
| CN203130602U (en) | Cross-flow fan for air conditioner, cross-flow blower and air conditioner | |
| CN203584898U (en) | Low-noise high-efficiency central air conditioner outdoor machine cooling axial-flow fan | |
| CN205639069U (en) | Movable vane, guiding subassembly and axial compressor cabinet -type air conditioner of axial compressor cabinet -type air conditioner | |
| CN201687736U (en) | Cross flow fan and air conditioner with same | |
| CN109595197B (en) | Fan | |
| WO2020103519A1 (en) | Centrifugal wheel, air conditioner, and assembly method for the centrifugal wheel | |
| CN103629156B (en) | A kind of central air conditioner outdoor unit but axial-flow blower of low-noise high-efficiency | |
| CN219865578U (en) | Centrifugal fan and air conditioner | |
| CN202679887U (en) | Wind-pressure enhanced radiating module | |
| CN201133384Y (en) | Cross-flow fan | |
| CN205190328U (en) | A machine in centrifugal fan and air conditioning for machine in air conditioning | |
| CN211737550U (en) | Backward centrifugal cross-section noise reduction type centrifugal fan blade | |
| CN208997043U (en) | Air-inlet grille and fan | |
| CN109595198B (en) | Fan impeller | |
| CN202418036U (en) | Axial flow fan and air conditioner with same | |
| CN207879691U (en) | Axial-flow windwheel and air conditioner | |
| CN219012968U (en) | Centrifugal fan blade, centrifugal fan and air conditioner |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |